EP1801455B1 - Manual or automated powershift transmission with three parallel shafts - Google Patents

Manual or automated powershift transmission with three parallel shafts Download PDF

Info

Publication number
EP1801455B1
EP1801455B1 EP06301217A EP06301217A EP1801455B1 EP 1801455 B1 EP1801455 B1 EP 1801455B1 EP 06301217 A EP06301217 A EP 06301217A EP 06301217 A EP06301217 A EP 06301217A EP 1801455 B1 EP1801455 B1 EP 1801455B1
Authority
EP
European Patent Office
Prior art keywords
gear
shaft
pinions
idling
pinion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP06301217A
Other languages
German (de)
French (fr)
Other versions
EP1801455A1 (en
Inventor
Michel Raoul
Philippe Rodrigues
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Renault SAS
Original Assignee
Renault SAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Renault SAS filed Critical Renault SAS
Publication of EP1801455A1 publication Critical patent/EP1801455A1/en
Application granted granted Critical
Publication of EP1801455B1 publication Critical patent/EP1801455B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds

Definitions

  • the invention relates to a manual or robotic gearbox of a motor vehicle.
  • It relates more particularly to a gearbox with parallel shafts and gears having a single primary shaft and two non-concentric secondary shafts driving the same differential ring.
  • a gearbox with parallel shafts and gear comprising a single primary shaft bearing a fixed set of teeth, and two non-concentric secondary shafts, which carry idler gears meshing with said fixed teeth and likely to be coupled selectively with the shaft that carries them by coupling devices to engage the different ratios of the box.
  • the present invention aims to provide a gearbox comprising only one primary shaft, allowing in particular to have six forward gears with consecutive passes under torque.
  • a synchronization and interconnection device is arranged between the first and reverse idle gears, and that the coupling devices of the idle gears of the ratios of rank higher than one are self-tapered couplers.
  • the crazy gears ratios higher rank to one of the same parity being grouped by two with the exception of the second crazy gear that is isolated.
  • the first idler gear is mounted on a freewheel.
  • the gearbox 10 illustrated by the figures 1 and 2 comprises a first primary shaft 20 rotatably mounted in a housing (not shown), and driven by a motor via a clutch 40 of simple conventional type, dry or wet.
  • the gearbox also comprises a first secondary shaft 50, said low, and a second secondary shaft 60, said high, also rotatably mounted in the housing.
  • Gears are arranged between the primary shaft 20 and the secondary shafts 50 and 60, so as to transmit the torque of the vehicle to a ring gear (not shown) of a differential (not shown) driving the wheels of a vehicle.
  • each secondary shaft comprises a down gear 51 and 61, which meshes with the differential ring.
  • the gears are formed of fixed teeth 21, 22, 23, 24, and the toothing of the idler gear 25 carried by the primary shaft 20, which meshes with idle gears and a fixed gear borne by the secondary shafts 50 and 60.
  • these idle gears are capable of being selectively rotatably connected to the low secondary shafts 50 and 60, and to the primary 20 for the toothing 25, by means of coupling couplers of the self-assisted conical coupler type. independent, to make gears independent selectively corresponding to at least two forward gears and a reverse gear.
  • the coupling devices of the idler gears of ratios higher than one are self-assisting conical couplers, while the first idler gear can have a conventional type clutch coupler. In any case, this first idle gear must however be mounted on a freewheel.
  • the self-assisted conical couplers may be as described in the patent FR 2 821 652 . They are for example put into service by the electromechanical actuators, as described in the publication FR 2,813,935 , integrating the motion control and force control means applied to the coupling devices.
  • the commitment of the reports is obtained, if desired, by means of a control assembly device as described in the publications FR 2 833 331 and FR 2 820 484 having a passage axis actuated manually by the driver, and at least one other passage axis rotated by a drive unit.
  • the second toothing 21 of the shaft 20 meshes with a single idler gear 81 mounted on a freewheel 810, carried by the low secondary shaft 50 to form the first report.
  • the first toothing 22 meshes with an idle gear, the intermediate reverse gear 91 carried by the high secondary shaft 60, the intermediate gear 90 connected to the pinion 91 meshes with the pinion 82 carried by the low secondary shaft 50 to constitute the reverse gear.
  • the third fixed toothing 23 meshes with two idle gears 83 and 93, carried respectively by the low secondary shaft 50 and the secondary shaft. high 60, to constitute respectively the reports of fifth and sixth.
  • the fourth fixed gear 24 meshes with two idle gears 84 and 94 respectively carried by the low secondary shaft 50 and the high secondary shaft 60, to constitute the third and fourth ratio.
  • a first double clutching device 100 selectively allows the idler gear 81 to be selectively rotatably connected to the secondary shaft 50 to obtain the first gear ratio or the idler gear 82 to obtain the reverse gear ratio.
  • a first dual coupling device 101 (self-assist conical coupler) rotates the secondary gear 50 to the idler gear 84 to obtain the third gear ratio, or the idle gear 83 to obtain the fifth gear.
  • a second double coupling device 102 identical to the first one 101, makes it possible to selectively link in rotation to the secondary shaft 60 the idler gear 94 to obtain the fourth gear ratio, or the idler gear 93 to obtain the sixth gear.
  • a third simple coupling device 103 makes it possible to selectively link the idler gear 25 to the primary shaft 20 to obtain the second gear ratio.
  • These coupling devices provide six forward gears and a reverse gear.
  • the grouping of the sprockets of the same parity, and the ratio of second isolated, make it possible to make a passage under torque between the following ratios, or a break of torque for the jumps of reports, with the fact that the ratio of first remains always triggered by the presence of the free wheel on the same report. Thanks to these measures, the box can have six forward gears with shifts under torque, while having only one input shaft 20, connected to the engine by a single input clutch 40.
  • the distances between the axes of the primary shaft 20 and the axis of each secondary shaft 50, 60 may be different.
  • the lowering gears 51 and 61 meshing with the differential gear are preferably of the same size, and the idle gears 93 and 83 respectively of the sixth and fifth gear ratios are different, as are the gears 84 and 94 for respectively the third and fourth ratios.
  • This arrangement is less advantageous because it does not allow to use the same idle gears 83 and 93 for the fifth and the sixth for the third and the fourth 84 and 94, but it allows to use the same pinions 51 and 61 .
  • the aforementioned distances may also be identical.
  • identical coupling devices and idler gears can be used for different ratios.
  • the gables 93 of the sixth report and 83 of the fifth report may be identical as well as the gears 84 and 94 for respectively the third and fourth reports.
  • the lowering gears 51 and 61 meshing with the differential ring then have a different number of teeth, the ratio of the number of teeth of two gears 51 and 61 corresponding in this case to the jump of the fourth, third and sixth ratios. on fifth.
  • the routing of the engine torque to the differential ring gear on the reverse gear is as follows.
  • the torque is transmitted from the motor to the primary shaft 20 by the clutch 40 closed.
  • the path of the engine torque to the differential ring on the first report is as follows.
  • the torque is transmitted from the motor to the primary shaft 20 by the closed clutch 40, then from the fixed toothing 21 to the idler gear 81, then the idler gear 81 to the secondary shaft 50 by the double clutch 100 in the clutch-on position. the pinion 81, and finally, the secondary shaft 50 to the fixed gear 51, which transmits it to the crown.
  • the path of the engine torque to the differential ring on the second gear is as follows.
  • the torque is transmitted from the motor to the primary shaft 20 by the clutch 40 closed, then the idler gear 25 coupled to the primary shaft via the coupling device 103 (self-assist conical coupler) coupled to the fixed gear 85, then the fixed gear 85 to the secondary shaft 50, and finally, the secondary shaft 50 fixed gear 51, which transmits it to the crown.
  • the torque path on the third gear is as follows.
  • the torque is transmitted from the motor to the primary shaft 20 by the clutch 40 closed.
  • the fixed toothing 24 to the idler gear 84 which transmits the torque to the low secondary shaft 50 via the double coupling device 101, which transmits the torque through the pinion gear 51 to the ring gear.
  • the torque path on the fourth gear is as follows.
  • the torque is transmitted from the motor to the primary shaft 20 by the clutch 40 closed.
  • the fixed toothing 24 to the idler gear 94 which transmits the torque to the high secondary shaft 60 via the double coupling device 102, which transmits the torque, via the pinion gear 61, to the crowned.
  • the torque path on the fifth gear is as follows.
  • the torque is transmitted from the motor to the primary shaft 20 by the clutch 40 closed.
  • the fixed toothing 23 to the idler gear 83 which transmits the torque to the low secondary shaft 50 through the double coupling device 101, which transmits the torque through the pinion gear 51 to the ring gear.
  • the torque path on the sixth gear is as follows.
  • the torque is transmitted from the motor to the primary shaft 20 by the clutch 40 closed.
  • the fixed toothing 23 to the idler gear 93 which transmits the torque to the high secondary shaft 60 through the double coupling device 102, which transmits the torque through the pinion gear 61 to the ring gear.
  • the first and reverse ratios are arranged on the high secondary shaft 60. It is the same odd reports.
  • the distances between the axes of the primary shaft 20 and secondary shafts 50 and 60 are equal.
  • the pinion gear 61 then has fewer teeth than the pinion 51.
  • the fixed gear 85 of the second gear ratio remains on the low secondary shaft 51.

Abstract

The gearbox has a double clutching device (100) rotatively connecting idle pinions (81, 82) with a secondary shaft (50) to obtain first and reverse gears respectively. An auto assisted conic coupler (101) rotatively connects idle pinions (83, 84) with the shaft (50), to obtain sixth and fourth gears respectively. An auto assisted conic coupler (102) rotatively connects idle pinions (93, 94) with the shaft (60), to obtain fifth and third gears respectively. An auto assisted conic coupler (103) rotatively connects an idle pinion (25) with a main shaft (20), for obtaining a second gear.

Description

L'invention concerne une boîte de vitesses manuelle ou robotisée de véhicule automobile.The invention relates to a manual or robotic gearbox of a motor vehicle.

Elle concerne plus particulièrement une boîte de vitesses à arbres parallèles et à engrenages comportant un seul arbre primaire et deux arbres secondaires non concentriques entraînant une même couronne de différentiel.It relates more particularly to a gearbox with parallel shafts and gears having a single primary shaft and two non-concentric secondary shafts driving the same differential ring.

Plus précisément, elle a pour objet une boîte de vitesses à arbres parallèles et à engrenages comprenant un seul arbre primaire portant un ensemble de dentures fixes, et deux arbres secondaires non concentriques, qui portent des pignons fous engrenant avec lesdites dentures fixes et susceptibles d'être couplés sélectivement avec l'arbre qui les porte par des dispositifs de couplage pour engager les différents rapports de la boîte.More specifically, it relates to a gearbox with parallel shafts and gear comprising a single primary shaft bearing a fixed set of teeth, and two non-concentric secondary shafts, which carry idler gears meshing with said fixed teeth and likely to be coupled selectively with the shaft that carries them by coupling devices to engage the different ratios of the box.

Par la publication EP 00 46 373 , qui montre toutes les caractéristiques du préambule de la revendication indépendante 1, on connaît une telle boîte de vitesses, dans laquelle les deux arbres secondaires entraînent un même pignon de sortie par deux pignons de descente.By publication EP 00 46 373 , which shows all the features of the preamble of the independent claim 1, there is known such a gearbox, wherein the two secondary shafts drive the same output gear by two pinions of descent.

On connaît par ailleurs, de la publication EP 1 273 825 , une boîte de vitesses, dans laquelle les pignons fous de rang supérieur à un sont associés à des coupleurs coniques αuto-αssistés, de manière à passer les rapports correspondants sous couple. Toutefois, la disposition proposée dans cette publication ne permet de disposer que de cinq rapports de marche avant.It is also known from the publication EP 1 273 825 , a gearbox, in which the idle gears of rank higher than one are associated with αuto-αssistés conical couplers, so as to pass the corresponding ratios under torque. However, the provision proposed in this publication allows only five forward reports.

La présente invention vise à réaliser une boîte de vitesses ne comprenant qu'un seul arbre primaire, permettant notamment de disposer de six rapports de marche avant à passages consécutifs sous couple.The present invention aims to provide a gearbox comprising only one primary shaft, allowing in particular to have six forward gears with consecutive passes under torque.

Dans ce but, elle propose qu'un dispositif de synchronisation et de crabotage soit disposé entre les pignons fous de première et de marche arrière, et que les dispositifs de couplage des pignons fous des rapports de rang supérieur à un soient des coupleurs coniques auto-assistés, les pignons fous des rapports de rang supérieur à un de même parité étant groupés par deux à l'exception du pignon fou de deuxième qui est isolé.For this purpose, it proposes that a synchronization and interconnection device is arranged between the first and reverse idle gears, and that the coupling devices of the idle gears of the ratios of rank higher than one are self-tapered couplers. assisted, the crazy gears ratios higher rank to one of the same parity being grouped by two with the exception of the second crazy gear that is isolated.

De préférence, le pignon fou de première est monté sur une roue libre.Preferably, the first idler gear is mounted on a freewheel.

Grâce à ces dispositions, tous les changements de rapports consécutifs de cette boîte peuvent s'effectuer sous couple, bien qu'elle ne possède qu'un seul arbre d'entrée relié au moteur par un seul embrayage d'entrée.Thanks to these provisions, all the consecutive shifts of this box can be under torque, although it has only one input shaft connected to the engine by a single input clutch.

D'autres caractéristiques et avantages de l'invention apparaîtront clairement à la lecture de la description suivante d'un mode de réalisation de celle-ci, en se reportant aux dessins annexés, sur lesquels

  • la figure 1 est une vue schématique en coupe à plans rabattus passant par les axes des arbres secondaire haut, primaire et secondaire bas, selon un premier mode de réalisation de la boîte proposée, où les entraxes primaire / secondaires sont différents, avec des pignons d'attaque de couronne de différentiel de même taille, et un groupe de première marche arrière sur l'arbre secondaire bas,
  • la figure 2 est une vue analogue d'un second mode de réalisation de l'invention, où les entraxes primaire / secondaires sont identiques, avec des pignons d'attaque de couronne de différentiel de taille différentes, et un groupe de première marche arrière sur l'arbre secondaire haut, et
  • les figures 3 et 4, indiquent les pignons utilisés sur chaque rapport respectivement sur les figures 1 et 2.
Other features and advantages of the invention will become clear from reading the following description of an embodiment thereof, with reference to the accompanying drawings, in which:
  • the figure 1 is a schematic sectional view with folded planes passing through the axes of the secondary high, primary and secondary low trees, according to a first embodiment of the proposed box, where the primary / secondary spacings are different, with pinions of attack of differential ring of the same size, and a first-gear group on the low secondary shaft,
  • the figure 2 is a similar view of a second embodiment of the invention, where the primary / secondary spacings are identical, with different size differential crown drive gears, and a group of first reverse gear on the shaft secondary high, and
  • the figures 3 and 4 , indicate the gears used on each report respectively on the figures 1 and 2 .

La boîte de vitesses 10 illustrée par les figures 1 et 2 comporte un premier arbre primaire 20 monté à rotation dans un carter (non représenté), et entraîné par un moteur par l'intermédiaire d'un embrayage 40 de type classique simple, sec ou humide. La boîte de vitesses comporte aussi un premier arbre secondaire 50, dit bas, et un deuxième arbre secondaire 60, dit haut, également mont és à rotation dans le carter.The gearbox 10 illustrated by the figures 1 and 2 comprises a first primary shaft 20 rotatably mounted in a housing (not shown), and driven by a motor via a clutch 40 of simple conventional type, dry or wet. The gearbox also comprises a first secondary shaft 50, said low, and a second secondary shaft 60, said high, also rotatably mounted in the housing.

Des engrenages sont agencés entre l'arbre primaire 20 et les arbres secondaires 50 et 60, de manière à transmettre le couple du véhicule à une couronne (non représenté) d'un différentiel (non représenté) entraînant les roues d'un véhicule. A cet effet, chaque arbre secondaire comporte un pignon de descente 51 et 61, qui engrène avec la couronne du différentiel.Gears are arranged between the primary shaft 20 and the secondary shafts 50 and 60, so as to transmit the torque of the vehicle to a ring gear (not shown) of a differential (not shown) driving the wheels of a vehicle. For this purpose, each secondary shaft comprises a down gear 51 and 61, which meshes with the differential ring.

Les engrenages sont const it ués de dent ures fixes 21, 22, 23, 24, et de la denture du pignon fou 25 portés par l'arbre primaire 20, qui engrènent avec des pignons fous et un pignon fixe portés par les arbres secondaires 50 et 60. Conformément à l'invention, ces pignons fous sont susceptibles d'être sélectivement liés en rotation aux arbres secondaires bas 50 et haut 60, et au primaire 20 pour la denture 25, par des moyens de couplage de type coupleur conique auto assisté indépendants, pour réaliser des engrenages indépendants correspondant sélectivement à au moins deux rapports de marche avant et un rapport de marche arrière. Conformément à l'invent ion, les dispositifs de couplage des pignons fous des rapports de rang supérieur à un, sont des coupleurs coniques auto assistés, tandis que le pignon fou de première peut disposer d'un coupleur à crabot de type conventionnel. Dans tous les cas, ce pignon fou de première doit cependant être monté sur une roue libre.The gears are formed of fixed teeth 21, 22, 23, 24, and the toothing of the idler gear 25 carried by the primary shaft 20, which meshes with idle gears and a fixed gear borne by the secondary shafts 50 and 60. According to the invention, these idle gears are capable of being selectively rotatably connected to the low secondary shafts 50 and 60, and to the primary 20 for the toothing 25, by means of coupling couplers of the self-assisted conical coupler type. independent, to make gears independent selectively corresponding to at least two forward gears and a reverse gear. In accordance with the invention, the coupling devices of the idler gears of ratios higher than one are self-assisting conical couplers, while the first idler gear can have a conventional type clutch coupler. In any case, this first idle gear must however be mounted on a freewheel.

De façon non limitative, les coupleurs coniques auto assistés peuvent être tels que décrits dans le brevet FR 2 821 652 . Ils sont par exemple mis en service par les actionneurs électromécaniques, tels que décrits dans la publication FR 2 813 935 , intégrant les moyens de contrôle de mouvement et d'efforts appliqués aux dispositifs de couplage. L'engagement des rapports est obtenu, si on le souhaite, à l'aide d'un dispositif d'ensemble de commande tel que décrit dans les publications FR 2 833 331 et FR 2 820 484 comportant un axe de passage actionné manuellement par le conducteur, et au moins un autre axe de passage déplacé en rotation par une unité motrice.In a nonlimiting manner, the self-assisted conical couplers may be as described in the patent FR 2 821 652 . They are for example put into service by the electromechanical actuators, as described in the publication FR 2,813,935 , integrating the motion control and force control means applied to the coupling devices. The commitment of the reports is obtained, if desired, by means of a control assembly device as described in the publications FR 2 833 331 and FR 2 820 484 having a passage axis actuated manually by the driver, and at least one other passage axis rotated by a drive unit.

Sur les figures 1 et 3, la seconde denture 21 de l'arbre 20 engrène avec un unique pignon fou 81 monté sur une roue libre 810, porté par l'arbre secondaire bas 50, pour constituer le rapport de première. La première denture 22 engrène avec un pignon fou, le pignon 91 intermédiaire de marche arrière porté par l'arbre secondaire haut 60, dont le pignon intermédiaire 90 lié au pignon 91 engrène avec le pignon 82 porté par l'arbre secondaire bas 50 pour constituer le rapport de marche arrière. La troisième denture fixe 23 engrène avec deux pignons fous 83 et 93, portés respectivement par l'arbre secondaire bas 50 et l'arbre secondaire haut 60, pour constituer respectivement les rapports de cinquième et de sixième. Le quatrième pignon fixe 24 engrène avec deux pignons fous 84 et 94 portés respectivement par l'arbre secondaire bas 50 et l'arbre secondaire haut 60, pour constituer le rapport de troisième et de quatrième.On the figures 1 and 3 , the second toothing 21 of the shaft 20 meshes with a single idler gear 81 mounted on a freewheel 810, carried by the low secondary shaft 50 to form the first report. The first toothing 22 meshes with an idle gear, the intermediate reverse gear 91 carried by the high secondary shaft 60, the intermediate gear 90 connected to the pinion 91 meshes with the pinion 82 carried by the low secondary shaft 50 to constitute the reverse gear. The third fixed toothing 23 meshes with two idle gears 83 and 93, carried respectively by the low secondary shaft 50 and the secondary shaft. high 60, to constitute respectively the reports of fifth and sixth. The fourth fixed gear 24 meshes with two idle gears 84 and 94 respectively carried by the low secondary shaft 50 and the high secondary shaft 60, to constitute the third and fourth ratio.

Enfin, la cinquième denture montée en pignon fou 25 sur l'arbre primaire 20, engrène avec un pignon fixe 85, porté par l'arbre secondaire 50, pour constituer le rapport de deuxième.Finally, the fifth toothing mounted on the idler shaft 25 on the primary shaft 20, meshes with a fixed gear 85, carried by the secondary shaft 50 to form the second gear.

Un premier dispositif de crabotage double 100 permet de lier sélectivement en rotation à l'arbre secondaire 50 le pignon fou 81, pour obtenir le rapport de première, ou le pignon fou 82, pour obtenir le rapport de marche arrière.A first double clutching device 100 selectively allows the idler gear 81 to be selectively rotatably connected to the secondary shaft 50 to obtain the first gear ratio or the idler gear 82 to obtain the reverse gear ratio.

Un premier dispositif de couplage double 101 (coupleur conique auto assisté) permet de lier en rotation à l'arbre secondaire 50 le pignon fou 84 pour obtenir le rapport de troisième, ou le pignon fou 83 pour obtenir le rapport de cinquième.A first dual coupling device 101 (self-assist conical coupler) rotates the secondary gear 50 to the idler gear 84 to obtain the third gear ratio, or the idle gear 83 to obtain the fifth gear.

Un second dispositif de couplage double 102, identique au premier 101, permet de lier sélectivement en rotation à l'arbre secondaire 60 le pignon fou 94 pour obtenir le rapport de quatrième, ou le pignon fou 93 pour obtenir le rapport de sixième. Enfin, un troisième dispositif de couplage simple 103 permet de lier sélectivement en rotation à l'arbre primaire 20, le pignon fou 25, pour obtenir le rapport de deuxième.A second double coupling device 102, identical to the first one 101, makes it possible to selectively link in rotation to the secondary shaft 60 the idler gear 94 to obtain the fourth gear ratio, or the idler gear 93 to obtain the sixth gear. Finally, a third simple coupling device 103 makes it possible to selectively link the idler gear 25 to the primary shaft 20 to obtain the second gear ratio.

Ainsi, seul le coupleur conique du rapport de deuxième est porté par l'arbre primaire 20, tandis que les autres coupleurs coniques sont agencés sur les deux arbres secondaires 50, 60, et qu'un dispositif de synchronisation et de crabotage classique, est disposé entre les pignons fous de première et de marche arrière.Thus, only the conical coupler of the second ratio is carried by the primary shaft 20, while the other conical couplers are arranged on the two secondary shafts 50, 60, and a conventional synchronization and clutching device, is arranged between the crazy gears of first and reverse.

Ces dispositifs de couplage permettent d'obtenir six rapports avant et un rapport de marche arrière. Le groupement des pignons de même parité, et le rapport de deuxième isolé, permettent de réaliser un passage sous couple entre les rapports qui se suivent, ou une rupture de couple pour les sauts de rapports, avec le fait que le rapport de première reste toujours enclenché grâce à la présence de la roue libre sur ce même rapport. Grâce à ces mesures, la boîte peut disposer de six rapports de marche avant avec des changements de rapport sous couple, tout en n'ayant qu'un seul arbre d'entrée 20, relié au moteur par un seul embrayage d'entrée 40.These coupling devices provide six forward gears and a reverse gear. The grouping of the sprockets of the same parity, and the ratio of second isolated, make it possible to make a passage under torque between the following ratios, or a break of torque for the jumps of reports, with the fact that the ratio of first remains always triggered by the presence of the free wheel on the same report. Thanks to these measures, the box can have six forward gears with shifts under torque, while having only one input shaft 20, connected to the engine by a single input clutch 40.

Conformément aux figures 1 et 2, les distances entre les axes de l'arbre primaire 20 et l'axe de chaque arbre secondaire 50, 60, peuvent être différentes.In accordance with figures 1 and 2 the distances between the axes of the primary shaft 20 and the axis of each secondary shaft 50, 60 may be different.

Dans cette configuration, les pignons de descente 51 et 61 engrenant avec la couronne de différentiel, sont de préférence de même taille, et les pignons fous 93 et 83 respectivement des rapports de sixième et de cinquième sont différents, ainsi que les pignons 84 et 94 pour respectivement les rapports de troisième et quatrième. Cette disposition est moins avantageuse car elle ne permet pas d'utiliser les mêmes pignons fous 83 et 93 pour la cinquième et la sixième pour la troisième et la quatrième 84 et 94, mais elle permet d'utiliser des mêmes pignons de descente 51 et 61.In this configuration, the lowering gears 51 and 61 meshing with the differential gear are preferably of the same size, and the idle gears 93 and 83 respectively of the sixth and fifth gear ratios are different, as are the gears 84 and 94 for respectively the third and fourth ratios. This arrangement is less advantageous because it does not allow to use the same idle gears 83 and 93 for the fifth and the sixth for the third and the fourth 84 and 94, but it allows to use the same pinions 51 and 61 .

Sans sortir du cadre de l'invention, les entraxes précités peuvent aussi être identiques. Dans ce mode de réalisation préféré, on peut ut iliser des dispositifs de couplage et des pignons fous identiques pour des rapports différents. Ainsi, les pignons 93 du rapport de sixième et 83 du rapport de cinquième peuvent être identiques ainsi que les pignons 84 et 94 pour respectivement les rapports de troisième et quatrième. En revanche, les pignons de descente 51 et 61 engrenant avec la couronne de différentiel ont alors un nombre de dents différent, le rapport du nombre de dents de deux pignons 51 et 61 correspondant dans ce cas, au saut des rapports quatrième sur troisième et sixième sur cinquième.Without departing from the scope of the invention, the aforementioned distances may also be identical. In this preferred embodiment, identical coupling devices and idler gears can be used for different ratios. So, the gables 93 of the sixth report and 83 of the fifth report may be identical as well as the gears 84 and 94 for respectively the third and fourth reports. On the other hand, the lowering gears 51 and 61 meshing with the differential ring then have a different number of teeth, the ratio of the number of teeth of two gears 51 and 61 corresponding in this case to the jump of the fourth, third and sixth ratios. on fifth.

En se référant aux figures 1 et 3, le cheminement du couple du moteur à la couronne de différentiel sur le rapport de marche arrière est le suivant. Le couple est transmis du moteur à l'arbre primaire 20 par l'embrayage 40 fermé. Puis, de la denture fixe 22 au premier pignon intermédiaire de marche arrière 91 lié au second pignon intermédiaire 90, puis du second pignon intermédiaire de marche arrière 90 au pignon fou 82 de marche arrière qui le transmet à l'arbre secondaire 50 par l'intermédiaire du crabot double 100 en position crabotée sur le pignon 82 de l'arbre secondaire bas 50 qui le transmet, par l'intermédiaire du pignon de descente 51, à la couronne.Referring to figures 1 and 3 , the routing of the engine torque to the differential ring gear on the reverse gear is as follows. The torque is transmitted from the motor to the primary shaft 20 by the clutch 40 closed. Then, fixed teeth 22 to the first intermediate reverse gear 91 connected to the second intermediate gear 90, then the second intermediate reverse gear 90 to the idler gear 82 which sends back to the secondary shaft 50 by the intermediate of the double claw 100 in the clutching position on the pinion 82 of the low secondary shaft 50 which transmits it through the pinion gear 51 to the crown.

Le cheminement du couple du moteur à la couronne de différentiel sur le rapport de première est le suivant. Le couple est transmis du moteur à l'arbre primaire 20 par l'embrayage 40 fermé, puis de la denture fixe 21 au pignon fou 81, puis du pignon fou 81 à l'arbre secondaire 50 par le crabot double 100 en position craboté sur le pignon 81, et enfin, de l'arbre secondaire 50 au pignon fixe 51, qui le transmet à la couronne.The path of the engine torque to the differential ring on the first report is as follows. The torque is transmitted from the motor to the primary shaft 20 by the closed clutch 40, then from the fixed toothing 21 to the idler gear 81, then the idler gear 81 to the secondary shaft 50 by the double clutch 100 in the clutch-on position. the pinion 81, and finally, the secondary shaft 50 to the fixed gear 51, which transmits it to the crown.

Le cheminement du couple du moteur à la couronne de différentiel sur le rapport de deuxième est le suivant. Le couple est transmis du moteur à l'arbre primaire 20 par l'embrayage 40 fermé, puis du pignon fou 25 couplé à l'arbre primaire via le dispositif de couplage 103 (coupleur conique auto assisté) couplé au pignon fixe 85, puis du pignon fixe 85 à l'arbre secondaire 50, et enfin, de l'arbre secondaire 50 au pignon fixe 51, qui le transmet à la couronne.The path of the engine torque to the differential ring on the second gear is as follows. The torque is transmitted from the motor to the primary shaft 20 by the clutch 40 closed, then the idler gear 25 coupled to the primary shaft via the coupling device 103 (self-assist conical coupler) coupled to the fixed gear 85, then the fixed gear 85 to the secondary shaft 50, and finally, the secondary shaft 50 fixed gear 51, which transmits it to the crown.

Le cheminement de couple sur le rapport de troisième est le suivant. Le couple est transmis du moteur à l'arbre primaire 20 par l'embrayage 40 fermé. Puis de la denture fixe 24 au pignon fou 84, qui transmet le couple à l'arbre secondaire bas 50 par l'intermédiaire du dispositif de couplage double 101, qui transmet le couple par l'intermédiaire du pignon de descente 51 à la couronne.The torque path on the third gear is as follows. The torque is transmitted from the motor to the primary shaft 20 by the clutch 40 closed. Then the fixed toothing 24 to the idler gear 84, which transmits the torque to the low secondary shaft 50 via the double coupling device 101, which transmits the torque through the pinion gear 51 to the ring gear.

Le cheminement de couple sur le rapport de quatrième est le suivant. Le couple est transmis du moteur à l'arbre primaire 20 par l'embrayage 40 fermé. Puis de la denture fixe 24 au pignon fou 94, qui transmet le couple à l'arbre secondaire haut 60 par l'intermédiaire du dispositif de couplage double 102, qui transmet le couple, par l'intermédiaire du pignon de descente 61, à la couronne.The torque path on the fourth gear is as follows. The torque is transmitted from the motor to the primary shaft 20 by the clutch 40 closed. Then the fixed toothing 24 to the idler gear 94, which transmits the torque to the high secondary shaft 60 via the double coupling device 102, which transmits the torque, via the pinion gear 61, to the crowned.

Le cheminement de couple sur le rapport de cinquième est le suivant. Le couple est transmis du moteur à l'arbre primaire 20 par l'embrayage 40 fermé. Puis de la denture fixe 23 au pignon fou 83, qui transmet le couple à l'arbre secondaire bas 50 par l'intermédiaire du dispositif de couplage double 101, qui transmet le couple par l'intermédiaire du pignon de descente 51 à la couronne.The torque path on the fifth gear is as follows. The torque is transmitted from the motor to the primary shaft 20 by the clutch 40 closed. Then the fixed toothing 23 to the idler gear 83, which transmits the torque to the low secondary shaft 50 through the double coupling device 101, which transmits the torque through the pinion gear 51 to the ring gear.

Le cheminement de couple sur le rapport de sixième est le suivant. Le couple est transmis du moteur à l'arbre primaire 20 par l'embrayage 40 fermé. Puis de la denture fixe 23 au pignon fou 93, qui transmet le couple à l'arbre secondaire haut 60 par l'intermédiaire du dispositif de couplage double 102, qui transmet le couple par l'intermédiaire du pignon de descente 61 à la couronne.The torque path on the sixth gear is as follows. The torque is transmitted from the motor to the primary shaft 20 by the clutch 40 closed. Then the fixed toothing 23 to the idler gear 93, which transmits the torque to the high secondary shaft 60 through the double coupling device 102, which transmits the torque through the pinion gear 61 to the ring gear.

Dans le mode de réalisation des figures 2 et 4, les rapports de première et de marche arrière sont agencés sur l'arbre secondaire haut 60. Il en est de même des rapports impairs. Les distances entre les axes de l'arbre primaire 20 et des arbres secondaires 50 et 60 sont égales. Le pignon d'attaque 61 possède alors moins de dents que le pignon 51. Le pignon fixe 85 du rapport de deuxième reste sur l'arbre secondaire bas 51.In the embodiment of figures 2 and 4 , the first and reverse ratios are arranged on the high secondary shaft 60. It is the same odd reports. The distances between the axes of the primary shaft 20 and secondary shafts 50 and 60 are equal. The pinion gear 61 then has fewer teeth than the pinion 51. The fixed gear 85 of the second gear ratio remains on the low secondary shaft 51.

L'avantage de cette disposition des pignons, est une facilité de réalisation de la commande d'engagement des rapports, notamment la commande du groupe de synchronisation et de crabotage 106 des rapports de première et de marche arrière dont l'axe de passage manuel est en partie supérieure de la boîte, alors que selon l'architecture des figures 1 et 3, la commande doit contourner l'ensemble des pignons. Cette disposition facilite la réalisation de la commande interne, car elle se situe en position haute de la boîte.The advantage of this arrangement of the gears, is an ease of realization of the gear engagement control, including the control of the synchronization group and interconnection 106 of the first and reverse gear whose axis of manual passage is in the upper part of the box, whereas according to the architecture of the figures 1 and 3 , the control must bypass all the gears. This arrangement facilitates the realization of the internal control, because it is in the upper position of the box.

Pour le reste, l'architecture et le fonctionnement de la boîte des figures 2 et 4, est similaire à celui des figures 1 et 3.For the rest, the architecture and the operation of the box of figures 2 and 4 , is similar to that of figures 1 and 3 .

Claims (7)

  1. Gearbox with parallel shafts and gears, comprising a single primary shaft (20) connected to the engine by a single input clutch (40) bearing a collection of fixed tooth sets (21, 22, 23, 24) and two non-concentric secondary shafts (50, 60) which bear idling pinions that mesh with said fixed tooth sets and can be coupled selectively to the shaft that bears them by coupling devices in order to engage the various gear ratios of the box, the two secondary shafts driving one and the same differential annulus gear, via two respective step-down pinions (51, 61) thereon, characterized in that the gear changes are performed under torque, in that a synchromesh and claw coupling device (100) is positioned between the first gear idling pinion (81) and the reverse gear idling pinion (82), and in that the coupling devices (101, 102, 103) for the idling pinions of the ratios of rank greater than one are auto-assisted conical couplers, the idling pinions for the gear ratios of rank higher than one of the same parity (83, 84; 93, 94) being grouped in twos with the exception of the second gear idling pinion (25) which is by itself.
  2. Gearbox according to Claim 1, characterized in that the first gear idling pinion (81) is mounted on a free wheel (810).
  3. Gearbox according to Claim 1 or 2, characterized in that the second gear conical coupler (103) is borne by the primary shaft (20) whereas the other conical couplers (101, 102) are positioned on the two secondary shafts (50, 60).
  4. Gearbox according to one of the preceding claims, characterized in that the inter-axis distances between each secondary shaft (50, 60) and the primary shaft (20) differ, and in that the two pinions (51, 61) that act on the differential annulus gear are identical.
  5. Gearbox according to Claim 4, characterized in that all the idling pinions of the odd-numbered gear ratios (81, 83, 84) and the fixed second-gear pinion (85) are on one secondary shaft (50), whereas the pinions (93, 94) of the other even-numbered gear ratios are on the other secondary shaft (60).
  6. Gearbox according to one of Claims 1 to 3, characterized in that the inter-axis distances between each secondary shaft (50, 60) and the primary shaft (20) are the same, and in that the two pinions (51, 61) that act on the differential annulus gear are of different sizes.
  7. Gearbox according to Claim 6, characterized in that the group comprising first gear and reverse gear is on the top secondary shaft.
EP06301217A 2005-12-22 2006-12-05 Manual or automated powershift transmission with three parallel shafts Not-in-force EP1801455B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0554013A FR2895481B1 (en) 2005-12-22 2005-12-22 MANUAL OR ROBOTIC GEARBOX WITH PASSAGE UNDER COUPLE WITH THREE PARALLEL TREES

Publications (2)

Publication Number Publication Date
EP1801455A1 EP1801455A1 (en) 2007-06-27
EP1801455B1 true EP1801455B1 (en) 2009-04-08

Family

ID=36917357

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06301217A Not-in-force EP1801455B1 (en) 2005-12-22 2006-12-05 Manual or automated powershift transmission with three parallel shafts

Country Status (4)

Country Link
EP (1) EP1801455B1 (en)
AT (1) ATE428071T1 (en)
DE (1) DE602006006141D1 (en)
FR (1) FR2895481B1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101012867B (en) * 2007-01-23 2011-08-03 黄昌国 Mechanically auto-shifting transmission
FR2939175B1 (en) * 2008-12-03 2011-04-01 Renault Sas TRANSMISSION GEARBOX UNDER COUPLE WITH THREE PARALLEL TREES.
WO2015096710A1 (en) * 2013-12-27 2015-07-02 山东核电设备制造有限公司 Personnel airlock system and side drive apparatus thereof
CN107355517A (en) * 2017-09-11 2017-11-17 赣州经纬科技股份有限公司 A kind of transmission mechanism of six speed transmission
CN113685501B (en) * 2020-05-18 2024-03-22 广州汽车集团股份有限公司 Ten-gear double-clutch transmission and vehicle

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU7366581A (en) * 1980-08-14 1982-02-18 Automotive Products Ltd. Transmission
US4461188A (en) * 1981-12-23 1984-07-24 Ford Motor Company Dual clutch multiple countershaft transmission
EP0463373A3 (en) 1990-06-29 1992-03-25 Texas Instruments Incorporated Local interconnect using a material comprising tungsten
IT1311757B1 (en) * 1999-03-19 2002-03-19 Moto Guzzi S P A LONGITUDINAL GEARBOX, IN PARTICULAR FOR MOTORCYCLES
EP1067312B1 (en) * 1999-07-05 2001-12-12 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Six speed transmission for motor vehicles
FR2799252B1 (en) * 1999-10-01 2002-05-03 Renault TWO-SECONDARY SHAFT GEARBOX
FR2813935B1 (en) 2000-09-08 2002-11-29 Renault TRANSMISSION WITH TRANSMISSION ACTUATOR
FR2820484B1 (en) 2001-02-02 2003-04-04 Renault MECHANICAL GEARBOX WITH PASSAGE ACTUATORS AND CORRESPONDING COUPLING DEVICE
FR2821652B1 (en) 2001-03-02 2003-04-18 Renault FRICTION CONE COUPLING DEVICE FOR GEARBOXES
FR2826701B1 (en) * 2001-06-29 2003-09-26 Renault GEARBOX WITH PARALLEL SHAFTS AND CORRESPONDING GEAR CHANGE CONTROL METHOD
FR2833331B1 (en) 2001-12-07 2004-05-14 Renault AUTOMATED GEARBOX WITH COUPLED PASSAGES
FR2841956B1 (en) * 2002-07-05 2005-01-21 Peugeot Citroen Automobiles Sa MOTOR VEHICLE WITH FREE WHEEL ON THE FIRST RECEIVER GEAR
DE10360075A1 (en) * 2003-01-09 2004-07-22 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Parallel manual gearbox for all-wheel drive has two input shafts with own couplings to engine-driven shaft, parallel output shaft, gearwheels/shift devices, output gearwheel driving two drive shafts
FR2852651B1 (en) 2003-03-17 2006-04-07 COMPACT GEARBOX WITH TWO CLUTCHES
FR2869571B1 (en) * 2004-04-29 2007-06-22 Renault Sas HYBRID POWER UNIT AND METHOD OF OPERATION

Also Published As

Publication number Publication date
DE602006006141D1 (en) 2009-05-20
FR2895481B1 (en) 2009-05-22
FR2895481A1 (en) 2007-06-29
ATE428071T1 (en) 2009-04-15
EP1801455A1 (en) 2007-06-27

Similar Documents

Publication Publication Date Title
FR2944079A1 (en) TRANSMISSION WITH DOUBLE CLUTCH AT SEVEN SPEEDS
FR2945849A1 (en) DUAL-SPEED DOUBLE-CLUTCH TRANSMISSION WITH FOUR AXES OF ROTATION
FR2945599A1 (en) Multiple speed transmission i.e. seven speed transmission, has dual clutch assembly including clutches selectively engaging with clutch housing for connecting one of transmission input shafts with corresponding synchronizer assemblies
EP1801455B1 (en) Manual or automated powershift transmission with three parallel shafts
EP1815163A1 (en) Double-clutch gearbox, in particular for motor vehicle
FR2930978A1 (en) DOUBLE CLUTCH GEARBOX COMPRISING TRANSFER LINKS BETWEEN PRIMARY TREES.
EP0969225A2 (en) Twin-countershaft transmission with two input clutches
FR2976039A3 (en) Double clutch gearbox for vehicle e.g. commercial vehicle, has input shafts and two secondary shafts, where one of input shafts carries set of fixed gears for determining ratio of first and second gear and third and fourth gear
EP1471282B1 (en) Compact transmission with two clutches
EP1798445B1 (en) Manual or automated powershift transmission with four parallel shafts
FR2846064A1 (en) Automobile gearbox comprises concentric solid and hollow primary shafts and two secondary shafts with pinions of same differential crown wheel, solid primary shaft fixed teeth meshing with idler pinions carried by secondary shafts
FR2855229A1 (en) Gear box for use in motor vehicle, has secondary shaft holding drive pinion directly attaching ring gear, and another secondary shaft driving ring gear on former secondary shaft by counter shaft
WO2017068256A1 (en) Hybrid transmission for a motor vehicle
EP1471283A2 (en) Compact double clutch gearbox with two clutches and two countershafts
EP1467123B1 (en) Gearbox for an automobile
EP2194293B1 (en) Gearbox shifting under torque with three parallel shafts
EP2359030B1 (en) Gearbox with an auxiliary shaft for first gear and reverse
FR2861447A1 (en) Gearbox for motor vehicles driving system, has jaw clutching to couple set of pinions on their shafts for selection of pinions, where pinions for first gear and reverse gear are driven by respective primary shafts
FR2847013A1 (en) Compact automobile gearbox comprises concentric solid and hollow primary shafts with fixed teeth, two secondary shafts with drive pinions for same differential crown wheel, primary shaft teeth meshing with secondary shaft idler pinions
FR2859004A1 (en) Compact gearbox with seven forward gears has first of two secondary shafts equipped with driving pinion for axle crown wheel to which shaft is connected by flexible element
WO2000036318A1 (en) Compact gearbox with two output shafts
FR2893689A1 (en) Motor vehicle gearbox, has secondary shaft with main synchronizing system to secure rotation of drive and main gear pinions, and intermediate shaft with intermediate synchronizing system to secure rotation of intermediate gear pinions
FR2855228A1 (en) MANUAL GEARBOX WITH THREE PARALLEL SHAFTS
FR2780760A1 (en) Gearbox with primary and twin parallel secondary shafts and a duel clutch configuration
FR2886701A1 (en) Gear box for e.g. simple clutch, has forward gear pinions engaged with one of fixed pinions, where forward gear pinions and their selective coupling units are centered on six transversal gear planes

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17P Request for examination filed

Effective date: 20071018

17Q First examination report despatched

Effective date: 20071119

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 602006006141

Country of ref document: DE

Date of ref document: 20090520

Kind code of ref document: P

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090908

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090719

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090808

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090708

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

26N No opposition filed

Effective date: 20100111

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090708

BERE Be: lapsed

Owner name: RENAULT SAS

Effective date: 20091231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100701

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091231

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090709

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091205

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091009

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090408

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101231

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20101231

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20151211

Year of fee payment: 10

Ref country code: GB

Payment date: 20151221

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20151221

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602006006141

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20161205

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20170831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170102

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161205

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170701